CN107667278B - Piston rotating device of self-weight pressure gauge - Google Patents
Piston rotating device of self-weight pressure gauge Download PDFInfo
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- CN107667278B CN107667278B CN201680031248.1A CN201680031248A CN107667278B CN 107667278 B CN107667278 B CN 107667278B CN 201680031248 A CN201680031248 A CN 201680031248A CN 107667278 B CN107667278 B CN 107667278B
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L7/00—Measuring the steady or quasi-steady pressure of a fluid or a fluent solid material by mechanical or fluid pressure-sensitive elements
- G01L7/16—Measuring the steady or quasi-steady pressure of a fluid or a fluent solid material by mechanical or fluid pressure-sensitive elements in the form of pistons
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L19/00—Details of, or accessories for, apparatus for measuring steady or quasi-steady pressure of a fluent medium insofar as such details or accessories are not special to particular types of pressure gauges
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- General Physics & Mathematics (AREA)
- Measuring Fluid Pressure (AREA)
- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
Abstract
The invention provides a piston rotating device of a self-weight pressure gauge, which initially rotates by a driving force and then is converted into free rotation, and can minimize errors of measured values caused by friction. The piston rotating device of the deadweight pressure gauge of the invention comprises: a driving wheel provided to the base and rotated by a rotational force of a motor; a driving rotor ring rotatably provided on an outer peripheral surface of a lower end portion of the main column; a power transmission part transmitting a rotational force of the driving wheel to a driving rotor ring; a hook rotatably provided in the driving rotor ring so as to protrude in a centrifugal force direction and to be inserted in the centrifugal force direction; an auxiliary rotating ring rotatably installed on the outer circumferential surface of the lower end portion of the main column, installed on the upper portion of the driving rotor ring, protruding downward, and provided with a start pin in a direction protruding the hook to be engaged; and the hanging and clamping protrusion is arranged on the lower side of the flange of the weight bell in a protruding mode and is arranged in a mode of hanging and clamping in the state that the hook protrudes to the maximum extent.
Description
Technical Field
The present invention relates to a piston rotating device for a weight manometer, and more particularly, to a piston rotating device for a weight manometer, which initially rotates by a driving force and then converts the rotation into free rotation.
Background
In general, a pressure gauge is a device for measuring the pressure of a liquid or gas and is classified into a liquid column type pressure gauge, a weight pressure gauge, a mechanical deformation gauge, and the like.
Among the above, the weight gauge uses a method of measuring pressure using a balanced state of force, and is used as a gauge for the first time (a calibration gauge or a calibration pressure generator) in measuring oil pressure and air pressure.
The deadweight manometer measures pressure using a balance state between the mass of a piston and a weight placed on the piston and the pressure of a fluid applied to a cylinder, and measures the pressure against a standard pressure (P)S) The calculation of (c) is calculated by the following formula 1.
[ EQUATION 1 ]
In said equation 1, PS shows the standard pressure (unit: Pa), Sigma shows the mass of the piston, and the sum of the masses (unit: kg) of the weights loaded on the piston, g shows the local gravitational acceleration (unit: M/s)2) And A is the standard sectional area (unit:squaremeter) of the piston-cylinder body.
In the above formula 1, all terms other than the "Σ M" factor in the molecular terms refer to values or constants measured by the ambient environment measurement device. In the case of the Σ M term, the sum of the combinations of the magnitudes of the pressures (measurement points) is set differently.
In general, for a weight manometer, a pressure range (measurement range) is shown as the sum (Σ M) of the piston-cylinder sectional area (a) in the denominator term of the above formula 1 (standard pressure calculation formula) and the piston and weight mass of the numerator term.
For example, when a pressure medium is compressed by a pressure generator or the like, a piston is pushed upward, and at this time, a force (pressure) of pushing the medium is balanced with a force (F ═ M × g) of pressing a cross-sectional area of a piston-cylinder and the piston, and the pressure at this time is a standard pressure (PS ═ F/a).
The force (F) produced by the mass (M) of the piston and the local gravitational acceleration (g) can only occur by friction with the cylinder by mechanical means. In order to minimize the friction, a method of rotating the piston is used.
Korean registered patent publication No. 10-0982284, No. 10-0284161, and the like disclose techniques of deadweight pressure gauges of various types for rotating a piston.
In the pressure gauge of the type in which the piston is rotated by the driving force of a conventional motor or the like, a constant amount of force and a constant rotation speed can be maintained, and since the rotation is guided by the mechanical contact, friction due to the rotation driving structure occurs in addition to friction between the piston and the cylinder, and during the operation of the self-weight pressure gauge, gravitational acceleration (g) is received and acts as a disturbance element, and thus, there is a concern that an error may be increased when the pressure is generated and maintained.
Korean registered patent publication No. 10-0806959, etc. discloses a technique for reducing friction by moving a cylinder up and down. For example, a structure is provided in which a piezoelectric disk and an elastic body having a thickness that changes in accordance with application of a power source are provided, and friction is reduced by moving a cylinder up and down without rotating a piston.
As described above, in the case of moving the cylinder, the moving distance is greatly limited, and moreover, it is difficult to sufficiently obtain the effect of reducing friction.
Disclosure of the invention
Technical problem to be solved by the invention
The present invention has been made to solve the above-mentioned problems of the prior art, and an object of the present invention is to provide a piston rotating device of a self-weight pressure gauge which minimizes an error in a measured value.
Means for solving the problems
In order to solve the above problem, the present inventors have initially performed rotation by a driving force and further converted the rotation into free rotation, thereby minimizing an error in a measurement value caused by an increase in friction.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the piston rotating apparatus of the deadweight manometer of the embodiment of the present invention, the driving force generated by the forward rotation of the motor is transmitted, the driving rotor ring rotates, as the driving rotor ring rotates, the front surface of the hook is hung on the actuating pin and rotates in the centrifugal force direction to protrude the hook, the front surface of the hook is hung on the hanging and catching protrusion, and the weight bell also rotates together with the driving rotor ring. At this time, the piston pressed in close contact by the weight bell also rotates together, and kinetic friction is generated between the piston and the cylinder, thereby minimizing resistance generated by friction.
Further, according to the piston rotating device of the self-weight pressure gauge of the embodiment of the present invention, after the forward rotation of the motor is stopped, the driving rotor ring is reversely rotated by the reverse rotation, the hook is separated in a state of being in close contact with the engaging projection and the actuating pin, and separated in a state of being in close contact with the hook, the hook is inserted by being rotated in a centripetal direction by the elastic force of the elastic member and the contact with the release pin, and the weight bell is switched to the freely rotatable state.
Therefore, the piston rotating device of the deadweight pressure gauge according to the embodiment of the present invention initially rotates by the driving force, but freely rotates in a state of rotating to some extent, thereby maintaining a constant speed by a constant amount of force, and minimizing friction that is otherwise generated by structural contact between the hooking protrusion and the hook when driven by an external force.
Drawings
FIG. 1 is a sectional view showing a piston rotating device of a deadweight manometer according to an embodiment of the present invention;
fig. 2 is a partially enlarged, partially cross-sectional view showing a piston rotating device of the deadweight manometer according to an embodiment of the present invention;
fig. 3 is a plan view for explaining an operation state of a hook of a piston rotating device of the deadweight manometer according to an embodiment of the present invention.
Preferred embodiments of the invention
The invention relates to a piston rotating device of a dead weight pressure gauge, in particular to a dead weight pressure gauge comprising a base, a cylindrical main column, a cylinder body, a piston cover and a weight bell, wherein the cylindrical main column is internally provided with a flow path for pressure medium to move and is arranged in a state of being vertical to the base; the cylinder body is arranged inside the upper end part of the main column; the piston is inserted into the cylinder body in a sliding manner; the piston cover is arranged at the upper end part of the piston and is arranged in a state of being separated from the upper end part of the main column; the weight bell, with the main column setting interval to the parcel outer peripheral face, and press with from above the outlying mode setting of piston lid, and support the flange that is used for the survey and the weight of dress and set up in the lower tip, this dead weight manometer's piston rotary device includes:
a driving wheel provided to the base and rotated by a rotational force of a motor;
a driving rotor ring rotatably provided on an outer peripheral surface of a lower end portion of the main column;
a power transmission part transmitting a rotational force of the driving wheel to a driving rotor ring;
a hook rotatably provided in the driving rotor ring so as to protrude in a centrifugal force direction and to be inserted in the centrifugal force direction;
an auxiliary rotating ring rotatably installed on the outer circumferential surface of the lower end portion of the main column, installed on the upper portion of the driving rotor ring, protruding downward, and provided with a start pin in a direction protruding the hook to be engaged;
and the hanging and clamping protrusion is arranged on the lower side of the flange of the weight bell in a protruding mode and is arranged in a mode of hanging and clamping in the state that the hook protrudes to the maximum extent.
The present invention is characterized in that 2 to 4 hooking projections, hooks, and actuating pins are provided at positions corresponding to each other at equal intervals.
In addition, the present invention is characterized in that a release pin is provided on the auxiliary rotating ring at an interval of 30 to 90 ° in a rear direction of the hook corresponding to the start pin.
Further, the present invention is characterized in that an elastic member for applying a force is provided to the driving rotor ring so as to be inserted into the hook in a centripetal direction.
In addition, the present invention is characterized in that, when the motor stops rotating in the forward direction, the motor temporarily rotates in reverse.
Further, the present invention is characterized in that the battery is connected in parallel with the power source supplied during the forward rotation, and the motor is instantaneously rotated in the reverse direction only by the power source charged in the battery at the instant of power-off.
In addition, the present invention is characterized in that the reverse rotation time of the motor is sensed by a sensor, and when the reverse rotation time is shorter than a predetermined time, the reverse rotation time is increased by supplying power thereto, and when the reverse rotation time is longer than the predetermined time, the reverse rotation is stopped by cutting off the power.
Detailed Description
Hereinafter, preferred embodiments of the piston rotating device of the deadweight pressure gauge according to the present invention will be described in detail with reference to the accompanying drawings.
The present invention can be implemented in various forms, and is not limited to the embodiments described below.
In the following description, for the sake of clarity, specific description of parts not closely related to the present invention is omitted, and the same or similar components are given the same reference numerals throughout the description, and repetitive description thereof is omitted.
First, as shown in fig. 1 and 2, the piston rotating device of the self-weight pressure gauge according to an embodiment of the present invention is applied to a self-weight pressure gauge including a base (10), a main column (20), a cylinder (30), a piston (40), a piston cap (50), and a weight bell (60).
The main column (20) is fixedly arranged in a state of being perpendicular to the base (10).
The main column (20) is formed in a cylindrical shape having a thickness, and a flow path (24) through which a pressure medium moves is formed inside.
The cylinder (30) is disposed inside the upper end of the main column (20).
The piston (40) is slidably inserted into the cylinder (30).
The piston cover (50) is provided at an upper end portion of the piston (40).
The piston cover (50) is provided so as to rotate and move integrally with the piston (40).
The piston cover (50) is set in a spaced state so as to avoid friction with the upper end of the main column (20).
The weight bell (60) is spaced apart from the main column (20) and is disposed so as to wrap the outer circumferential surface of the main column (20).
The weight bell (60) is formed in a cylindrical shape.
A flange (64) for supporting a weight to be loaded for measurement is annularly projected from the outer peripheral surface of the lower end of the weight bell (60).
The weight bell (60) is formed such that the periphery of the piston cover (50) is pressed from above.
In the weight manometer configured as described above, when a weight is loaded on the weight bell (60), a downward pressing force acts on the piston cap (50) according to the weight of the weight and the weight bell (60), and a vertical force acts on the piston cap (50) and the piston (40) so as to move downward.
The base (10), the main column (20), the cylinder (30), the piston (40), the piston cap (50), and the weight bell (60) can be implemented by applying the structure of a commonly used weight gauge, and thus, detailed description thereof is omitted.
A piston rotating apparatus of a deadweight manometer according to an embodiment of the present invention, as shown in fig. 1 to 3, includes: the driving wheel (120), the driving rotor ring (140), the power transmission part (130), the hook (150), the auxiliary rotating ring (160) and the hanging and clamping protrusion (170).
The driving wheel (120) is rotatably provided to the base (10).
The driving wheel (120) is connected with the shaft of the motor (110).
The driving wheel (120) is rotated by the rotational force of the motor (110).
The driving rotor ring (140) is rotatably provided on the outer peripheral surface of the lower end portion of the main column (20).
For example, the driving rotor ring (140) is rotatably provided on the outer peripheral surface of the main column (20) via a bearing (190).
The power transmission part (130) performs a function of transmitting the rotational force of the driving wheel (120) to the driving rotor ring (140).
The power transmission member (130) can be formed using a belt.
Besides a transmission belt, gears, chains, or the like can be used as the power transmission member (130).
A transmission belt groove (148) can also be formed at the driving rotor ring (140) to enable more accurate power transmission of the power transmission part (130), i.e., the transmission belt.
The hook (150) is rotatably provided to the driving rotor ring (140).
For example, the hook (150) is rotatably disposed to the driving rotor ring (140) using a hinge pin (156).
The hook (150) is provided in the driving rotor ring (140) so as to protrude in the centrifugal force direction and so as to be inserted in the centripetal force direction.
A setting groove (145) into which the hook (150) is inserted is formed in the driving rotor ring (140), and the setting groove (145) is formed to have a size that limits a range in which the hook (150) rotates in a protruding direction.
The auxiliary rotating ring (160) is rotatably provided on the outer peripheral surface of the lower end portion of the main column (20).
For example, the auxiliary rotating ring (160) is rotatably provided on the outer peripheral surface of the main column (20) via a bearing (190).
The auxiliary rotating ring (160) is provided at an interval at an upper portion of the driving rotor ring (140).
An actuating pin (164) is provided to protrude downward from the auxiliary rotating ring (160) so that the hook (150) is hooked in the protruding direction.
The hanging and clamping protrusion (170) is arranged on the lower side of the flange (64) of the weight bell (60) in a protruding mode.
The hooking protrusion (170) is provided in such a manner that the hook (150) hooks in a state of maximum protrusion.
The front surface (152) of the hook (150) that engages with and contacts the engagement protrusion (170) and the activation pin (164) is formed so as to be aligned with the radial direction in a state where the hook (150) is maximally projected.
The size of the installation groove (145) formed in the drive rotor ring (140) is set so as to restrict the maximum protrusion state of the hook (150) (the state in which the front surface (152) is aligned with the radial direction).
In the state configured as described above, when the driving rotor ring (140) rotates in the counterclockwise direction as shown in fig. 3, and the actuating pin (164) contacts the front surface (152) of the hook (150) to catch, the hook (150) rotates in the clockwise direction around the hinge pin (156) and protrudes from the installation groove (145) of the driving rotor ring (140), and the catch protrusion (170) is caught in the front surface (152) of the hook (150) (shown by a solid line in fig. 3).
The hanging and clamping protrusions (170), the hooks (150) and the starting pins (164) are arranged at 2-4 positions corresponding to each other at equal intervals.
For example, the hooking protrusion (170), the hook (150) and the actuating pin (164) may be provided in two spaced relationship at a distance of 180 °.
As described above, when the catching protrusions 170 are disposed at equal intervals with the hooks 150 and the actuating pins 164, the rotational force of the driving rotor ring 140 is more accurately transmitted to the auxiliary rotating ring 160 and the weight bell 60 with minimizing the shaking.
Furthermore, a release pin (166) may be provided on the auxiliary rotating ring (160) so as to be spaced by 30 to 90 degrees toward the rear surface (154) of the hook (150) in correspondence with the start pin (164).
The rear face (154) of the hook (150) forms a jaw to catch the release pin (166).
In the state configured as described above, when the driving rotor ring (140) is rotated in the clockwise direction as shown in fig. 3, the release pin (166) is caught by the jaw on the rear surface (154) of the hook (150), and the hook (150) is rotated in the counterclockwise direction about the hinge pin (156) until a position not in contact with the catching projection (170) is inserted into the inside of the setting groove (145) (shown by a dotted line in fig. 3) of the driving rotor ring (140).
Furthermore, although not shown in the drawings, an elastic member for applying a force may be provided in the driving rotor ring (140) so as to be inserted into the hook (150) in a centripetal direction.
A torsion spring can also be used as the elastic member.
The outer circumferential surfaces of the driving rotor ring (140) and the auxiliary rotating ring (160) are formed to have a small diameter so as not to contact the catching protrusion (170).
The motor (110) is configured to rotate in the forward direction in the reverse direction temporarily.
For example, a battery (capacitor) is connected in parallel to a power supply supplied during forward rotation, and the motor (110) can be instantaneously rotated in the reverse direction only by the power supply charging the battery at the instant when the power supply is turned off.
Next, an operation of the piston rotating device of the weight manometer according to the embodiment of the present invention configured as described above will be described.
First, when the motor (110) is rotated in the positive direction, the rotational force of the motor (110) is transmitted to the driving rotor ring (140) through the driving wheel (120) and the power transmission member (130), and the driving rotor ring (140) is rotated in the counterclockwise direction as shown in fig. 3. At this time, the auxiliary rotating ring (160) and the weight bell (60) are in a stationary state.
As described above, the driving rotor ring (140) rotates counterclockwise (in the forward direction), the front surface (152) of the hook (150) contacts and is caught by the actuating pin (164) provided in the auxiliary rotating ring (160), the hook (150) rotates in the centrifugal force direction (clockwise direction as viewed in fig. 3) about the hinge pin (156) and protrudes from the installation groove (145) of the driving rotor ring (140), and the auxiliary rotating ring (160) can rotate together with the driving rotor ring (140). At this time, the weight bell (60) is in a static state.
As described above, when the driving rotor ring 140 and the auxiliary rotating ring 160 rotate, the front face 152 of the hook 150 is engaged by the engaging protrusion 170 provided on the weight bell 60, and the weight bell 60 also rotates together with the driving rotor ring 140. At this time, the piston cap (50) and the piston (40) which are pressed into close contact by the weight bell (60) also rotate together, and kinetic friction occurs between the piston (40) and the cylinder (30), thereby minimizing resistance due to friction.
Through the above-described process, the weight bell (60) is rotated, whereby, when the rotation speed (RPM) of the level (set level) required by the user is reached, the power supply to the motor (110) is cut off to stop the positive rotation of the motor (110).
Then, a reverse power source (for example, a power source for charging a capacitor) is supplied to the motor (110) to rotate the motor (110) in the reverse direction.
As described above, when the reverse rotation of the motor (110) occurs, the driving rotor ring (140) receives the transmitted rotational force of the motor (110) through the driving wheel (120) and the power transmission member (130) and rotates in a clockwise direction (reverse direction) as shown in fig. 3.
As described above, as the driving rotor ring (140) rotates in the clockwise direction, the front surface (152) of the hook (150) is spaced apart in a state of being in close contact with the catching protrusion (170) and the actuating pin (164).
As described above, when the front surface (152) of the hook (150) is spaced apart from the hook protrusion (170) and the actuating pin (164) in close contact with each other, the weight bell (60) and the auxiliary rotating ring (160) are not in a state in which the rotational force of the driving rotor ring (140) is transmitted, and thus the weight bell (60) and the auxiliary rotating ring (160) are continuously rotated counterclockwise (forward rotation) by inertia.
As the driving rotor ring 140 rotates in the clockwise direction, the rear surface 154 of the hook 150 is brought into contact with a release pin 166 provided in the auxiliary rotating ring 160 to be hooked, and the auxiliary rotating ring 160 rotates in the counterclockwise direction, so that the release pin 166 pushes the hook 150, the hook 150 rotates in the centripetal direction (the counterclockwise direction as viewed in fig. 3) about the hinge pin 156, and the hook 150 is inserted into the installation groove 145 of the driving rotor ring 140.
In the above, the auxiliary rotating ring (160) changes its rotating direction as the release pin (166) is caught by the rear surface (154) of the hook (150), and rotates clockwise (rotates reversely) together with the driving rotor ring (140). At this time, the weight bell (60) continues to rotate freely by inertia, and is kept rotating counterclockwise (rotating positively).
In contrast, when an elastic member such as a torsion spring is provided in the hook (150) instead of the release pin (166), when the hook (150) is separated from the hooking protrusion (170) and the activation pin (164) in a state of being in close contact with each other, an elastic force generated by the elastic member acts on the hook (150), and the hook (150) is inserted into the installation groove (145) of the driving rotor ring (140) by rotating in a centripetal direction (counterclockwise direction as viewed in fig. 3) about the hinge pin (156).
As described above, in the state where the hook (150) is inserted into the installation groove (145) of the drive rotor ring (140), when the drive rotor ring (140) and the auxiliary rotating ring (160) are rotated in the reverse direction, the hook protrusion (170) provided in the weight bell (60) is not in contact with the hook (150), and the rotational force of the drive rotor ring (140) is not transmitted to the weight bell (60).
Therefore, in the piston rotating device of the deadweight pressure gauge according to the embodiment of the present invention, which is configured and operated as described above, the rotation of the initial weight bell (60) and the piston (40) is performed by the rotation of the driving force of the motor (110), but the piston rotates freely in a state of forming a certain degree of rotation, so that a certain rotation speed can be maintained by a certain amount of force, and the additional friction caused by the structural contact between the hook (150) and the catch protrusion (170) when driven by an external force can be minimized.
In the above, the preferred embodiment of the piston rotating device of the weight manometer of the present invention has been described, but the present invention is not limited thereto, and various modifications can be made within the scope of claims, the description of the invention and the drawings, and the present invention falls within the scope of the present invention.
Industrial applicability
The present invention can be applied to a weight manometer and a device including the same.
Claims (6)
1. A piston rotating device of a dead weight pressure gauge relates to the dead weight pressure gauge comprising a base, a cylindrical main column, a cylinder body, a piston cover and a weight bell, wherein the cylindrical main column is internally provided with a flow path for pressure medium to move and is arranged in a state of being vertical to the base; the cylinder body is arranged inside the upper end part of the main column; the piston is inserted into the cylinder body in a sliding manner; the piston cover is arranged at the upper end part of the piston and is arranged in a state of being separated from the upper end part of the main column; the weight bell, which is spaced from the main column, wraps the outer circumference surface, is arranged in a manner of pressing the periphery of the piston cover from the upper surface, and supports a flange for measuring the weight arranged at the lower end part, the piston rotating device of the self-weight pressure gauge is characterized in that,
the method comprises the following steps:
a driving wheel provided to the base and rotated by a rotational force of a motor;
a driving rotor ring rotatably provided on an outer peripheral surface of a lower end portion of the main column;
a power transmission part transmitting a rotational force of the driving wheel to a driving rotor ring;
a hook rotatably provided in the driving rotor ring so as to protrude in a centrifugal force direction and to be inserted in the centrifugal force direction;
an auxiliary rotating ring rotatably installed on the outer circumferential surface of the lower end portion of the main column, installed on the upper portion of the driving rotor ring, protruding downward, and provided with a start pin in a direction protruding the hook to be engaged;
the hanging and clamping bulge is arranged at the lower side of the flange of the weight bell in a protruding manner and is arranged in a hanging and clamping mode under the state that the hook protrudes to the maximum extent;
wherein, when the motor stops rotating in the forward direction, the motor temporarily rotates in the reverse direction.
2. The piston rotating device of the self weight manometer according to claim 1,
the hanging and clamping protrusions, the hooks and the starting pins are arranged in 2-4 positions corresponding to each other at equal intervals.
3. The piston rotating device of the self weight manometer according to claim 1 or 2, wherein,
and a release pin is provided on the auxiliary rotating ring at an interval of 30 to 90 DEG in the rear direction of the hook corresponding to the start pin.
4. The piston rotating device of the self weight manometer according to claim 1 or 2, wherein,
an elastic member for applying force is provided at the driving rotor ring to be inserted into the hook in a centripetal direction.
5. The piston rotating device of the self weight manometer according to claim 1,
the storage battery is connected in parallel with a power supply supplied during forward rotation, and at the moment of cutting off the power supply, the motor is instantaneously rotated in reverse direction only by the power supply charged in the storage battery.
6. The piston rotating device of the self weight manometer according to claim 1,
the reverse rotation time of the motor is sensed by a sensor, and when the reverse rotation time is shorter than a predetermined time, the power supply is increased to increase the reverse rotation time, and when the reverse rotation time is longer than the predetermined time, the power supply is cut off to stop the reverse rotation.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR10-2015-0088992 | 2015-06-23 | ||
| KR1020150088992A KR101641081B1 (en) | 2015-06-23 | 2015-06-23 | Rotating Device for Piston of Deadweight Pressure Gauge |
| PCT/KR2016/006569 WO2016208938A1 (en) | 2015-06-23 | 2016-06-21 | Piston rotating device for deadweight pressure gauge |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107667278A CN107667278A (en) | 2018-02-06 |
| CN107667278B true CN107667278B (en) | 2020-04-14 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201680031248.1A Active CN107667278B (en) | 2015-06-23 | 2016-06-21 | Piston rotating device of self-weight pressure gauge |
Country Status (3)
| Country | Link |
|---|---|
| KR (1) | KR101641081B1 (en) |
| CN (1) | CN107667278B (en) |
| WO (1) | WO2016208938A1 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110186615B (en) * | 2019-05-09 | 2022-06-24 | 大连工业大学 | Rotary driving type piston pressure gauge |
| CN110186616B (en) * | 2019-05-09 | 2022-06-24 | 大连工业大学 | Piston pressure gauge for driving weight in friction-free mode |
| KR102150505B1 (en) | 2020-03-17 | 2020-09-03 | 주식회사 피디케이 | Post modules used in deadweight testers |
| CN114152386B (en) * | 2020-09-08 | 2024-08-23 | 北京康斯特仪表科技股份有限公司 | Single-piston type dynamic friction pressurizing and pressure regulating device |
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| KR20070010789A (en) * | 2005-07-20 | 2007-01-24 | 삼성전자주식회사 | Belt transmission apparatus |
| KR20150020799A (en) * | 2013-08-19 | 2015-02-27 | 김여일 | Wind generator system combined with sub-blades and over-running clutch for extending the life of the gearbox in wind turbine |
-
2015
- 2015-06-23 KR KR1020150088992A patent/KR101641081B1/en active IP Right Grant
-
2016
- 2016-06-21 WO PCT/KR2016/006569 patent/WO2016208938A1/en active Application Filing
- 2016-06-21 CN CN201680031248.1A patent/CN107667278B/en active Active
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| GB2273162A (en) * | 1992-12-03 | 1994-06-08 | Pierre Roger Delajoud | Pressure measurement: dead weight piston device |
| KR20000027175A (en) * | 1998-10-27 | 2000-05-15 | 양경돈 | Apparatus for measuring dropping distance of noncontact piston of poise pressure gauge |
| KR100806959B1 (en) * | 2006-08-31 | 2008-02-22 | 한국표준과학연구원 | Pressure balance with non-rotation piston |
| CN201476924U (en) * | 2009-07-30 | 2010-05-19 | 陕西创威科技有限公司 | Multifunctional figure displaying piston pressure gauge |
| CN201611297U (en) * | 2010-03-19 | 2010-10-20 | 北京中盛华旭电子科技有限公司 | Manometer piston rotation device |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN107667278A (en) | 2018-02-06 |
| WO2016208938A1 (en) | 2016-12-29 |
| KR101641081B1 (en) | 2016-07-20 |
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